Patent GB-1037680-A (GB)
Title: Improvements in or relating to disc brakes
IPC: F16D65/18
Filed: 1964-11-13
Abstract: 1,037,680. Disc brakes; fluid-pressure control of brakes. S.A. FRANCAISE DU FERODO. Nov. 13, 1964 [Dec. 19, 1963], No. 46371/64. Headings F2E and F2F. A disc brake, for use in a hydraulic braking system of the kind having a pair of balanced primary circuits feeding one pair of wheel brakes of a vehicle and a secondary circuit energized by the drag forces on these brakes, comprises a plate 38 rotatable about the axis of the disc and carrying on one side of the axis one or a pair of hydraulic cylinders (the fluid chambers of which are indicated at 52, 53), and on the other side of the axis a piston and cylinder arrangement providing two chambers 76, 77, the former of which is connected to the chambers 52, 53 and to an appropriate power chamber 22 or 24 of master cylinder 10, and the latter being connected as part of the secondary system. By this arrangement, the two front brakes 11, 12 of the vehicle provide power to apply the two rear brakes 13, 14 which are of the conventional construction shown. The production of pressure in the secondary system, by the drag forces acting on the pads, is thus augmented by chamber 76 when the disc is rotating in the forward direction F, but is reduced when the disc is rotating in the reverse direction, while, because the power chambers 22, 24 of the master cylinder are designed to deliver equal volumes of fluid, any differences between the coefficients of friction of either the brake linings or the road wheels associated with the two front brakes are compensated for through the action of chambers 76, 77, since a decrease in volume of the chamber 76 of one brake, should the friction become low, causes an increase in volume of the chamber 76 of the other front brake to reduce braking on this wheel. The secondary system is maintained filled with fluid by the triple reservoir 25 of the master cylinder via a valve 27, valves 26, 28 being associated with the power chambers 22, 24. The piston structure 18 of the master cylinder comprises pistons 19, 20 and 21, the pistons 19 and 21 being related in size such as to give equal displacements from the chambers 22, 24. Piston 20 is shown smaller than piston 19 so that a servo-effect is applied to the master cylinder. However, instead of this arrangement servo may be obtained by connecting the secondary system to the chambers 52, 53 or to additional chambers in the front brake operating cylinders (Fig. 4, not shown) in which case piston 20 is larger than piston 19. The front brake of Fig. 1 is disclosed in detail in Figs. 2 and 3 (not shown) and comprises pistons 45, 46 applying pads 49, 50, and pistons 59, 60 in a cylinder structure 42 providing the chambers 76, 77. The structure 42 is there shown mounted on the rotatable plate 38, while a tail 74 of piston 60 abuts piston 59 to form a stationary stack which is held by crutches 61, 62 between arms 63, 64 of a fixed plate 35 (also shown in Fig. 1) which carries mounting brackets 36 and a stub axle 34 on which the plate 38 and bearings 33 for the wheel and disc hub 32 are mounted. A spring 72 normally maintains a collar 68 on the piston 59 in contact with the casing of the cylinder structure 42 so that chamber 76 is at minimum volume and chamber 77 at maximum volume. The brake of Figs. 5 and 6 (not shown) is modified to suit the embodiment of Fig. 4 (not shown) by the provision of extra chambers 94, 95 in the pad-applying cylinders. Figs. 8 and 9 (not shown) disclose a modification including a floating caliper 100 whereby a single padapplying piston 46 may be used. Fig. 9 (not shown) discloses a modified arrangement of pistons 59, 60 adapted to move with the rotatable plate 38, the cylinder structure 42 being fixed. A floating piston 110 in this case replaces the tail of piston 60, this arrangement being said to give even better balancing as a result of smoother operation.